Mechanical first table drive assembly for a bale wagon

ABSTRACT

Each time after a predetermined number of bales have been positioned on a first or bale-receiving table pivotally mounted on the chassis of a bale wagon, a mechanical drive assembly, mounted on the wagon chassis and driven by an external power source such as the power takeoff of a tractor, causes pivotal movement of the first table forwardly along a path of revolution defined about an axis along which the table is pivotally mounted on the chassis from a lower, substantially horizontal, balereceiving position to an upper, substantially vertical, baledischarge position and then reversely back along the path to the bale-receiving position. A relatively low average angular velocity is imposed on the table by the mechanical drive assembly during an initial portion of the pivotal movement of the table forwardly along its path, a relatively high average velocity being imposed during an intermediate portion, and a relatively low average angular velocity being imposed during a final portion, whereby bales being carried by the table are imparted with an increasing momentum, and thereby effectively maintained at rest in a desired arrangement on the first table substantially as received thereon, during the initial and intermediate portions of the pivotal movement of the table from its bale-receiving position toward its bale-discharge position and are imparted with a decreasing momentum, and thereby deposited on a second or tierforming table of the bale wagon in the aforementioned arrangement, during the final portion of the first table movement when the first table reaches its bale-discharge position which arrangement enhances the efficient performance of the subsequent tier-forming operation of the second table.

United States Patent [19] Butler 1 Jan. 28, 1975 1 MECHANICAL FIRST TABLE DRIVE ASSEMBLY FOR A BALE WAGON [75] Inventor: Gene R. Butler, Kingsburg, Calif.

[73] Assignee: Sperry Rand Corporation, New

Holland, Pa.

22 Filed: Sept. 4, 1973 211 Appl. No.: 394,373

Willrodt...

Grey.......,..

Primary ExaminerRobert J. Spar Assistant Examiner-Gary Auton Attorney, Agent, or Firm-John R. Flanagan; Frank A. Seemar; Louis .1. Virelli, Jr.

[57] ABSTRACT Each time after a predetermined number of bales have been positioned on a first or bale-receiving table pivotally mounted on the chassis of a bale wagon, a mechanical drive assembly, mounted on the wagon chassis and driven by an external power source such as the power takeoff of a tractor, causes pivotal movement of the first table forwardly along a path of revolution defined about an axis along which the table is pivotally mounted on the chassis from a lower, substantially horizontal, bale-receiving position to an upper, substantially vertical, bale-discharge position and then reversely back along the path to the bale-receiving position. A relatively low average angular velocity is imposed on the table by the mechanical drive assembly during an initial portion of the pivotal movement of the table forwardly along its path, a relatively high average velocity being imposed during an intermediate portion, and a relatively low average angular velocity being imposed during a final portion, whereby bales being carried by the table are imparted with an increasing momentum, and thereby effectively maintained at rest in a desired arrangement on the first table substantially as received thereon, during the initial and intermediate portions of the pivotal movement of the table from its bale-receiving position toward its bale-discharge position and are imparted with a decreasing momentum, and thereby deposited on a second or tier-forming table of the bale wagon in the aforementioned arrangement, during the final portion of the first table movement when the first table reaches its bale-discharge position which arrangement enhances the efficient performance of the subsequent tier-forming operation of the second table.

3 Claims, 16 Drawing Figures PATENTED JAN? 8 75 SHEET 3 OF 6 MECHANICAL FIRST TABLE DRIVE ASSEMBLY FOR A BALE WAGON CROSS REFERENCES TO RELATED APPLICATIONS Reference is hereby made to the following copending U.S. applications dealing with related subject matter and assigned to the assignee of the present invention:

1. A Mechanical Drive for a Receiving Table on a Bale Wagon by Lee D. Butler et al., U.S. Ser. No. 393,867, filed Sept. 4, 1973, a division of U.S. Ser. No. 139,302, filed May 3, 1971, now abandoned.

2. Bale Wagon" by Donald M. Grey, et al., U.S. Ser. No. 392,138, filed Aug. 27, 1973, a continuation of U.S. Ser. No. 139,324, filed May 3, 1971, now abandoned.

3. Bale Wagon by Donald M. Grey, et al., U.S. Ser. No. 390,97l, filed Aug. 23, 1973, a division of U.S. Ser. No. 139,324, filed May 3, l97l, now abandoned.

BACKGROUND OF THE INVENTION 1. FIELD OF THE lNVENTlON The present invention relates generally to bale wagons or vehicles intended to handle baled products such as baled hay and more particularly is concerned with a bale wagon which is provided with a novel mechanical drive assembly for pivotally moving the first or balereceiving table of the wagon from its bale-receiving position to its bale-discharge position.

2. BACKGROUND OF THE PRIOR ART ln bale wagons of the type presently on the market, such as disclosed in U.S. Pat. No. 3,638,808, the first or bale-receiving table of the wagon generally is pivotally moved between a lower, substantially horizontal, bale-receiving position and an upper, substantially vertical, bale-discharge position by the operation of a hydraulic cylinder which is pivotally coupled between the chassis of the wagon and the first table.

There are several disadvantages in the use of a hydraulic cylinder as the means for pivotally moving the first table, the first disadvantage being the necessity of providing a self-contained hydraulic power unit on the bale wagon to operate the hydraulic cylinder and the second disadvantage being in the undesirable pattern of varying angular velocities imparted to the first table during its pivotal movement by the operation of the hydraulic cylinder.

With respect to the first of these disadvantages, it should be noted that bale wagons of the aforementioned type have a second or tier-forming table and a third or load-bearing table, as well as other components, which commonly utilize hydraulic units, such as cylinders and motors to actuate their respective operations.

Heretofore, it has not been possible to construct a bale wagon suitable for use with all farm tractors of the type having hydraulic accessories without having a selfcontained hydraulic power system on the wagon to operate the plurality of hydraulic units since many farm tractors of the aforementioned type do not have a sufficient number of remote hydraulic circuits to operate all of the hydraulic units.

Furthermore, even those tractors of the aforementioned type which have adequate remote hydraulic circuitry to operate all of the hydraulic cylinders do not necessarily have circuitry which delivers hydraulic fluid in the correct gallons per minute to properly operate the one hydraulic cylinder which causes the pivotal movement of the first table. Oftentimes, the hydraulic fluid is delivered at too high a rate to the one hydraulic cylinder whereby it pivots the first table too rapidly thereby imparting an excess of momentum to the bales resting thereon which causes the bales to be thrown or rolled too far onto the second table when the first table reaches the end of its movement which interferes with the efficient performance of the tier-forming operation of the second table. Conversely, the hydraulic fluid is delivered at too low a rate to the one hydraulic cylinder whereby it is not possible for the one hydraulic cylinder to pivot the first table rapidly enough for the first table to perform its intended function within the time period allotted to it which means that the bale wagon must be pulled around the hay field by the tractor at an undesirably slow speed in order to efficiently pickup bales from the ground and eventually form them into a stack on the load-bearing table of the wagon.

Therefore, up to the present, it has been necessary to provide a bale wagon of the type disclosed in the aforementioned U.S patent with a self-contained hydraulic power system for operating all of its hydraulic units in order to achieve the efficient performance of the various bale wagon operations at reasonably high speeds.

With respect to the second disadvantage, it should be noted that in bale wagons of the aforementioned type which have a self-contained hydraulic power system, or in tractors of the aforementioned type which have adequate remote hydraulic circuits for operating the hydraulic units of the bale wagon, a fixed displacement hydraulic pump has heretofore been generally utilized as the source of hydraulic power whereby the hydraulic cylinders operated thereby are moved at a constant linear velocity. Accordingly, the one hydraulic cylinder which pivotally moves the first table is operated at a constant linear velocity to cause the pivotal movement of the first table.

However, operation of the one hydraulic cylinder at a constant linear velocity is undesirable from the standpoint of the pattern of varying angular velocities im-' posed on the first table as it is pivotally moved from its bale-receiving position to its bale-discharge position by the one hydraulic cylinder, as will be explained hereinafter.

Since it has heretofore been found desirable to pivotally move the first table between a bale-receiving position in which it is disposed in a generally horizontal plane and a bale-discharge position in which it is disposed in a generally vertical plane in order to efficiently perform its assigned functions, and, therefore, for its pivotal movement between these positions to sweep an arc of approximately the one hydraulic cylinder which causes pivotal movement of the first table has commonly and apparently most advantageously been pivotally anchored to the wagon chassis at a point thereon which falls on a straight line which is generally tangent to the arc of movement of another point at which the one hydraulic cylinder is pivotally coupled to the first table at approximately the 45 mark therealong or mid point of the arc. The one hydraulic cylinder in being so mounted with respect to the first table and driven at a constant linear velocity imposes a higher average angular velocity to the table during an initial portion of its pivotal movement from its balereceiving position to its bale-discharge position, then a lower average angular velocity during a middle portion of its pivotal movement, and finally a higher average angular velocity again during a final portion of its pivotal movement. v

Such mounting arrangement of the hydraulic cylinder with respect to the first table, when compared to other possible arrangements, for example, where the point of tangency is at the 30 or 60 mark along, the arc has been found to achieve the optimum performance which one can expect from a hydraulic cylinder in terms of the motion it imposes on the table and imparts thereby to the bales, given its constant linear velocity of operation. However, the aforementioned pattern of varying angular velocities which the hydraulic cylinder imposes on the first table disadvantageously imparts an undesirably greater magnitude of momentum to the bales being carried by the table during the initial portion of its movement than that magnitude imparted during the intermediate portion of its movement which frequently causes the bales to bounce on the table and become laterally separated from each other and also imparts an undesirably greater momentum to the bales during the final portion of its movement than that magnitude imparted during the intermediate portion of its movement which frequently causes the bales to be thrown or rolled too far onto the second table of the wagon when the first table reaches the end of its movement at its vertical, bale-discharge position whereby the bales as deposited on the second table will not necessarily be resting on their desired side, that being the cut side rather than the twine side, and may likely be substantially separated laterally from each other which complicates or impedes the ability of the second table to deliver a neatly arranged layer of bales to the third table of the wagon during the performance of a subsequent, tier-forming operation.

Notwithstanding the aforementioned disadvantage of the one hydraulic cylinder in being operated at a constant linear velocity, up to the present time the advantages to be gained by the utilization ofa fixed displacement hydraulic pump which so operates the one hydraulic cylinder have outweighed the alternative approach of using a variable displacement pump which would operate the one hydraulic cylinder at a variable linear velocity and thereby possibly impose a more desirable pattern of varying angular velocities to the pivotal movement of the first table and, as a result, impart more desirable magnitudes of momentum to the bales being carried by the first table.

In particular, the significant advantages of the fixed displacement hydraulic pump over the variable displacement hydraulic pump from the standpoint of bale wagon production, for instance, in terms of the more simplified design and performance requirements, and the lower cost, of the self-contained hydraulic power system to be utilized by the wagon for the fixed displacement hydraulic pump over the self-contained hydraulic power system which would be required by the wagon for the variable displacement hydraulic pump have heretofore outweighed the possible advantage of the variable displacement hydraulic pump over the fixed displacement hydraulic pump from the standpoint of the more desirable pattern of motion which it imposes on the first table.

OBJECTS AND SUMMARY or THE INVENTION It is an object of the present invention, therefore, to provide a mechanical drive assembly for pivotally moving the first table which improves bale wagons of the aforementioned type in that the provision of the assembly will overcome all of the aforementioned disadvantages of the one hydraulic cylinder utilized heretofore to pivotally drive the first table.

More particularly, it is an object of the present invention to provide a mechanical drive assembly for pivoting the first table in place of the one hydraulic cylinder utilized heretofore.

It is another object of the present invention to provide a mechanical drive assembly for pivoting the first table, which by eliminating the use of the one aforementioned hydraulic cylinder, eliminates the necessity for a self-contained hydraulic power unit on the bale wagon so that the available remote hydraulic circuits of the tractor can be fully utilized to operate the remaining hydraulic cylinders which operate the second and third tables and other components of the wagon.

A further object of the present invention is to provide a mechanical drive assembly which pivotally moves the first table through a desirable pattern of varying angular velocities which imparts increasing momentum to the bales carried thereon to maintain the bales at rest in a desired arrangement on the table substantially as received thereon during its pivotal movement from its bale-receiving position toward its bale-discharge position and which appropriately reduces the momentum imparted to the bales during the final portion of movement of the table to achieve depositing of the bales on the second table in the aforementioned arrangement when the first table reaches its bale-discharge position which arrangement enhances theefficient performance of the subsequent tier-forming operation of the second table.

A still further object of the present invention is to provide a mechanical drive assembly which, although slightly more expensive than the one hydraulic cylinder it replaces, is significantly less costly than the selfcontained hydraulic power system the necessity for which it eliminates.

The above objects, and others which will be apparent to those skilled in the art, are accomplished by providing a mechanical drive assembly mounted on the bale wagon chassis which each time after a predetermined number of bales have been positioned on the first table of the wagon is automatically operatively coupled to the first table of the wagon for causing pivotal movement of the first table, through one complete cycle from a lower, substantially horizontal, bale-receiving position to an upper, substantially vertical, baledischarge position and then back to the bale-receiving position. The mechanical drive is comprised by a driving unit which includes a driving input component which is capable of being coupled to an external source of rotary power, such as the power takeoff of a tractor, and continuously rotatably driven thereby at a substantially constant rotational. velocity and a driven output component coupled to the first table which is capable of being inoperatively uncoupled from the driving input component and capable of being operatively coupled to, and driven by, the driving input component to cause the aforementioned pivotal movement of the first table through one complete cycle during a single rotation of the driving input component, and a control component for maintaining the driven output component inoperatively uncoupled from the driving input component prior to each time the predetermined number of bales have been positioned on the first table at its balereceiving position and for allowing operative coupling of the driven output component to the driving input component during a single rotation thereof each time after the predetermined number of bales have been positioned on the first table. The driven output component when operatively coupled to the driving input component during a single rotation cycle thereof imposes a relatively low average angular velocity on the first table during an initial portion of its pivotal movement from its bale-receiving position toward its baledischarge position, a relatively high average angular velocity during an intermediate portion thereof and a relatively low average angular velocity during a final portion thereof, whereby bales being carried by the first table are imparted with an increasing momentum, and thereby effectively maintained at rest in a desired arrangement on the table substantially as received thereon during the initial and intermediate portions of the pivotal movement of the first table from its balereceiving position toward its bale-discharge position and are imparted with a decreasing momentum, and thereby deposited on a second table of the wagon in the aforementioned arrangement during the final portion of the first table movement when the first table reaches its bale-discharge position which arrangement enhances the efficient performance of the subsequent tier-forming operation of the second table.

Other objects and attainments of the invention will become apparent to those skilled in the art upon a reading of the following detailed description when taken in conjunction with the drawings in which there is shown and described an illustrative embodiment of the invention; it is to be understood, however, that this embodiment is not intended to be exhaustive nor limiting of the invention but is given for purpose of illustration in order that others skilled in the art may fully understand the invention and the principles thereof and the manner of applying it in practical use so that they may modify it in various forms, each as may be best suited to the conditions of a particular use.

BRIEF DESCRIPTION OF THE DRAWINGS In the course of the following detailed description reference will be frequently made to the attached drawings in which:

FIG. 1 is a fragmentary top plan view of the forward end ofa bale wagon constructed in accordance with the principles of the present invention and showing a mechanical drive assembly for pivotally moving the first table of the bale wagon;

FIG. 2 is a side elevational view of the forward end of the bale wagon of FIG. 1;

FIG. 3 is an enlarged front elevational view as seen along line 33 of FIG. 1 showing the control component of the mechanical drive assembly in a locked condition in which it maintains the driven output component of the mechanical drive assembly inoperatively uncoupled from the driving input component of the mechanical drive assembly before the predetermined number of bales have been positioned on the first table;

FIG. 4 is a top plan view of the control component of FIG. 3;

FIG. 5 is a view similar to that of FIG. 3 but showing the control component in an unlocked condition in which it allows operative coupling of the driven output component to the driving input component after the predetermined number of bales have been positioned on the first table;

FIG. 6 is a top plan view of the control component of FIG. 5;

FIG. 7 is an enlarged front elevational view as seen along line 77 of FIG. 1 showing the driven output component in an operatively coupled relationship with the driving input component and causing pivotal movement of the first table towards its upper, bale-discharge position;

FIG. 8 is a view similar to that of FIG. 7 but showing the driven output component in another operatively coupled relationship with the driving input component which controls the reverse pivotal movement of the first table toward its initial, lower bale-receiving position;

FIGS. 9A through 9F are diagrammatic representations of the forward end of the bale wagon of FIG. 2 illustrating, in sequences covering equal time periods, the operation of the mechanical drive assembly, depicted in solid line, in pivotally moving the first table from the lower, bale-receiving position to the upper, bale-discharge position as compared to the operation of heretofore utilized hydraulic cylinder, depicted in broken line, in pivotally moving the first table through the same arc of movement between the aforementioned positions;

FIG. 10 is a diagrammatic representation of the respective paths of revolution of pointsof linkage of a connecting arm of the driven output component with a revolving crank arm thereof and with the receiving table of FIGS. 9A through 9F about respective axes of revolution thereof illustrating the approximate degrees of angular displacement of the respective points along their respective paths during consecutive, equal time periods with the corresponding positions of their respective points each being cross-referenced, and each respectively corresponding, to one of the solid line, diagrammatic representations the mechanical drive assembly and the first table of FIGS. 9A through 9F; and

FIG. 11 is a diagrammatic representation of the path of revolution of the point of linkage between the hydraulic cylinder and the first table of FIGS. 9A through 9F about the axis of revolution of the table and with respect to the pivotal axis at which the hydraulic cylinder is anchored to the bale wagon chassis illustrating the approximate degrees of angular displacement of the linkage point along its path during consecutive, equal time periods which are also equal to the time periods of FIG. 10, with the positions of the point each being cross-referenced, and each corresponding, to one of the broken line, diagrammatic representations of the hydraulic cylinder and the first table of FIGS. 9A and 9F. 9

DETAILED DESCRIPTION OF THE INVENTION IN GENERAL Referring now to FIGS. 1 and 2, there is shown a forward portion of an improved bale wagon, indicated generally by numeral 10, being of the general type disclosed originally in US. Pat. No. 2,848,127 and more recently in US. Pat. No. 3,638,808. The bale wagon 10 is provided with a chassis, indicated generally by numeral 12, the forward portion of which is only partially shown in FIGS. 1 and 2. The chassis 12 is formed of left and right longitudinally extending rails 14 of which only the left rail 14 is shown and cross rails (not shown) which interconnect the longitudinally extending rails 14 at their rearward portions. Although not specifically shown the rearward portions of the rails 14 are supported by a pair of wheels and the forward portions of the rails 14 converge together and merge into a clevis assembly which adapts the wagon to be secured to a tractor, or other towing vehicle, located at the front thereof.

Mounted at the forward portion of the chassis 12 and extending transversely thereto for pivotal movement about an axis A,, on the chassis 12 is a first or balereceiving table generally indicated by the numeral 16. A baler loader, although not shown, is mounted on the left side of the forward portion of the chassis 12 adjacent to the left end of the first table 16 and is adapted to elevate bales from the ground and laterally deflect them onto the first table 16 at its left end. A conveyor 18 is mounted on the left longitudinal rail 14 of the chassis 12 below the first table 16 and is adapted to assist the bale loader in positioning the bales upon the first table 16. The first table 16 is capable of receiving a predetermined number of bales, preferably two bales, successively at a given time from the bale loader. After receiving the two bales, the first table 16 is then capable of being pivotally moved about its axis A, through a complete cycle from its lower, substantially horizontal, bale-receiving position as shown in FIG. 9A to its upper, substantially vertical, bale-discharge position as shown in FIG. 9F and then back to its lower, balereceiving position. A forward, bale-receiving portion 20 of a second or tier-forming table 22 mounted on the chassis 12 is disposed generally co-planarly with, and rearwardly and upwardly from, the first table 16 when the first table 16 is at its bale-receiving position of FIGS. 2 and 9F and capable of receiving the bales from the first table 16 when the first table 16 is at its baledischarge position of FIG. 9A.

The specific details of the construction and operation of the bale-loader, the conveyor 18, the second table 22 and other known features of the bale wagon 10 need not be described in this application in order to properly understand the present invention. The disclosure of U.S. Pat. No. 3,638,808 provides an adequate detailed description of these features and is incorporated herein by reference thereto. The specific details of the construction of the first table 16, although adequately described in the aforementioned U.S. patent, are described in detail hereinafter in order to promote a thorough understanding of the present invention upon a reading of this application alone.

FIRST TABLE The first table 16 is comprised by a L-shaped structure which includes, as shown in FIG. 1 and 2, a pair of rear, upstanding leg portions 26 (of which only the left rear leg portion 26 is shown) being pivotally secured at their upper ends at 24 respectively to the upper ends of a pair of spaced, upstanding brackets 28 (of which only the left bracket 28 is shown) mounted on the rails 14 of the chassis 12, and a pair of forwardly extending leg portions 30 (of which only the left forward leg portion 30 is shown) across which are fixedly mounted two transversely extending beams 32,34 on which the two bales are intended to be received in a desired predetermined arrangement wherein the bales are restingpreferably on one of their wider. twine sides and in end-to-end relationship. Also, the first table 16 includes an arm 36 having a forward horizontal portion 38, which extends between and generally parallel to forwardly extending .leg portions 30 and is fixedly secured to the underside of the transverse beams 32,34, and a rearward inclined portion 40, which extends upwardly at an acute angle from the forward portion 38 and between the upstanding leg portions 26 to a free end 42. A pair of diagonal and inclined support braces 44 (of which only the left brace 44 is shown) are fixedly secured at their one ends to the forwardly extending leg portions 30 and at their opposite ends near the upper end of the rearward inclined portion 40 of the arm 36. MECHANICAL FIRST TABLE DRIVE ASSEMBLY The improvement in the bale wagon 10, being of the general type of bale wagon disclosed in the aforementioned patents, is constituted by a mechanical drive assembly, mounted on the chassis 12 and indicated generally by numeral 46, and its cooperative relationship with the first table 16 which provides for improved pivotal movement of the first table 16 between its aforementioned upper and lower positions.

The drive assembly 46 generally includes a driving unit, indicated generally by numeral 48, which may be operatively coupled to the first table 16 for pivotally moving the first table 16 through one complete cycle and a control component, indicated generally by numeral 50, for controlling the operative coupling of the driving unit 48 to the first table 16.

DRIVING UNIT The driving unit 48 of the assembly 46 is comprised by a driving input component, generally indicated as numeral 52, which includes a multiple gear-shaft drive train, generally indicated as numeral 54, and a first clutch member, generally indicated as numeral 56. The drive train 54 is rotatably mounted on the left longitudinal rail 14 of the chassis 12, capable of being operatively coupled at input shaft end 58 thereof to a source of continuous rotary power external to the bale wagon 10, preferably the power takeoff of the tractor used to pull the wagon, in any suitable manner such as disclosed in aforementioned U.S. Pat. No. 3,638,808, and capable of being continuously rotatably driven by the power takeoff at a constant rotational velocity. The first clutch member 56 includes a circular chain sprocket 58 rotatably driven through a drive chain 60 by another circular chain sprocket 62 fixedly attached on the output shaft end 64 of the drive train 54 for continuous driving rotation therewith. The first clutch member 56 also includes an annular ring portion 66 fixedly attached to the sprocket 58 for continuous rotation therewith and having a scallop-shaped inner periphery, generally indicated as numeral 68.

The driving unit 48 of the assembly 46 is further comprised by a driven output component, indicated generally as numeral 70, which includes a shaft 72 rotatable about an axis A which is generally spaced below and rearwardly from, and parallel to, axis A of the first table 16, a second clutch member, generally indicated as numeral 74, a crank arm 76 and linking member 78. The shaft 72 is rotatably mounted through a sleeve 80 being fixedly mounted transversely on the left longitudinal rail 14 of the chassis 12 with the first clutch member 56 being rotatably mounted on the shaft 72 at one of its ends. The second clutch member 74 is fixedly mounted on the shaft 72 near the aforementioned one of its ends for rotation therewith. Accordingly, the first and second clutch members 56,74 are mounted on the shaft 72 in close side-by-side relationship to each other, as clearly shown in FIG. 1, with the first clutch member 56 continuously rotating about axis A relative to the second clutch member 74 and the shaft 72. The crank arm 76 is fixedly mounted on the shaft 72 at an opposite one of its ends and extends outwardly therefrom to a free end 82 which revolves around the axis A The linking member 78 is pivotally coupled at one end to the free end 82 of the crank arm 76 at a point of linkage indicated as P and pivotally coupled at an opposite end to the free end 42 of the arm 36 of the first table 16 at a point of linkage indicated as P The driven output component 70 of the driving unit 48 may be selectively inoperatively uncoupled from the driving input component 52 of the driving unit 48 or operatively coupled to, and rotatably driven by, the driving input component 52 by the selective disengagement or engagement of the second clutch member 74 with the continuously rotating first clutch member 56 as controlled by control component 50.

To achieve engagement with the first clutch member 56, the second clutch member 74 includes a carrier plate 84 fixedly mounted to the shaft 72 for rotation therewith and having first and second pawl elements 86,88 pivotally connected at opposing ends of the plate 84 with rollers 90,92 respectively rotatably secured to the pawl elements 86,88 oppositely from the pivotal connections thereof with the plate 84. The rollers 90,92 are disposed on the sides of the pawl elements 86,88 facing the annular ring portion 66 of the first clutch member 56 and, in view of the aforementioned closely spaced, side-by-side relationship of the first and second clutch members 56,74, the rollers 90,92 each project within the interior of the annular ring portion 66 of the first clutch member 56, as clearly shown in FIG. 1. Each of the pawl elements 86,88 are pivotally movable from their respective inward positions as shown in FIG. 2 to respective positions angularly displaced outwardly therefrom toward the annular ring portion 66 as shown in FIG. 8.

Each recess 93 in the series of semi-circular recesses 93 comprising the scallop-shaped inner periphery 68 of the annular ring portion 66 is capable of receiving therewithin in a closely-fitted, engaged relationship a segment of one of the rollers 90,92 when the respective pawl elements 86,88 are disposed respectively in their outward position as shown in FIG. 8.

The first pawl element 86 also has a finger portion 94 projecting generally outwardly beyond the outer periphery 96 of the annular ring portion 66 in an opposite directional sense away from the pivotal connection of the first pawl element 86 with the plate 84 to that of the location of securement of the roller 90 from the pivotal connection of the first pawl element 86 and terminating at a tip 98. A spring 100 interconnects the finger portion 94 near its tip 98 and the one end of the plate 84 to which is pivotally connected the first pawl element 86 and biases the first pawl element 86 normally to its outward position toward the inner periphery 68 of the annular ring portion 66 where at such position the roller 90 is disposed in the aforementioned closely-fitted, engaged relationship with one of the recesses 93 in the periphery 68. It is readily apparent that when the first pawl element 86 is disposed at its outward position with its roller fitted within one of the recesses 93, angular driving force created by the clockwise rotation of the first clutch member 56 is transmitted through the first pawl element 86 to the plate 84 and causes the plate 84 and shaft 72 to rotate in clockwise fashion with the first clutch member 56, and the first pawl element to revolve, about axis A of the shaft 72. The shaft 72 and plate 84 will continuously rotate with the first clutch member 56 unless a stop element 102 operated by the control component 50 of the drive assembly 46, which component 50 will be described in detail hereinafter, has been positioned at a location along the path of revolution of the first pawl element 86 at which the stop element 102 blocks the path and engages the tip 98 of the finger portion 94 of the first pawl element 86 when the element 86 has revolved to the aforementioned location, as shown in FIG. 2. Engagement of the finger portion 94 of the first pawl element 86 by the stop element 102 causes the first pawl element 86 to pivot to its inward position against the bias imposed thereon by spring 100 and thereby disengage its roller 90 from one of the recesses 93 in the first clutch member 56 which prevents transmission of the driving force from the continuously rotating first clutch member 56 through the first pawl element 86 to the plate 84 of the second clutch member 74 whereby the plate 84 and the shaft are maintained at rest. Thus, selective inoperative uncoupling and operative coupling of the driven output component 70 of the driving unit 48 with the driving input component 52 is determined by whether or not the stop element 102 is positioned at the aforemention location blocking the path of revolution of the first pawl element 86.

The particular manner in which the roller 92 of the second pawl element 88 becomes engaged in one of the recesses 93 of the first clutch member 56 and the object of such engaged relationship will be discussed hereinafter in connection with the description of the operation of the first table 16 by the drive assembly 46. CONTROL COMPONENT As stated hereinabove, the location of the stop element 102 of the control component 50 in relation to path of revolution of the first pawl element 86 determines whether the driven output component 70 will be coupled or uncoupled from the driving input component 52 and, consequently, whether the driving unit 48 will be inoperatively uncoupled from, or operatively coupled to, the first table 16.

In addition to the stop element 102, the control component 50 includes a trip mechanism, generally indicated as number 104 in FIGS. 1 and 2, which is linked to the stop element 102 and biased to normallymaintain the stop element 102 at the aforementioned location blocking the path of revolution of the first pawl element 86.

As shown in FIGS. 1 and 2, and more particularly in FIGS. 3 0 6, the trip mechanism 104 includes a rightangled support plate 106 fixedly mounted to the left longitudinal rail 14 of the chassis l2 and having a horizontal plate portion 108 to which is pivotally mounted about a vertical axis a L-shaped latch 110 at a horizontal spaced position below the plate portion 108. The support plate 106 also has a vertical plate portion 112 which projects downwardly from one side of the hori' zontal plate portion 108 and has a horizontal, elongated slot 114 defined therein through which extends a tab portion 116 of the latch 110. The vertical plate portion 112 also extends beyond-one end of the horizontal plate portion 108 to provide a mounting tab 118.

Pivotally secured to the mounting tab 118 about a horizontal axis is a vertical locking plate 120 having a notch 122 defined in its upper end through which the tab portion 116 of the latch 108 further extends when the plate 120 is at its upper locking position as shown in FIGS. 3 and 4. The plate 120 at its lower end is coupled to a flange 123 by a rod 124 which is pivotally secured at its opposing ends respectively to the plate 120 and the flange 123. The flange 123 is fixedly mounted on one end ofa shaft 126 being rotatably mounted on the chassis 12 in a manner not shown, such as via conventional structure which mounts the conveyor 18 to the left longitudinal rail 14 of the chassis 12. A trip lever 128, shown in FIGS. 1 and 2 and in fragmentary dotted outline form in FIGS. 3 and 5, is fixedly secured to the opposite end of the rotatable shaft 126 and extends upwardly past transverse beam 34 of the first table 16 to a position thereabove. Deflection of the trip lever 128 is a counterclockwise direction downwardly toward the beam 34 which occurs when a bale is delivered onto the first table 16 by the conveyor 18 causes both shaft 126 and flange 123 fixed thereto to rotate counterclockwise. Such movement of the flange 123 from its position of FIGS. 3 and 4 counterclockwise to its position of FIGS. 5 and 6 causes pivotal movement of the plate 120 from its upper locking position of FIGS. 3 and 4 counterclockwise to its lower unlocking position of FIGS. 5 and 6.

The outer end of the tab portion 116 of the latch 110 which is disposed beyond the notch 122 of the locking plate 120 is coupled to a second trip lever 130 by a link rod 132 which is pivotally secured at its opposing ends respectively to the tab portion 116 and the second trip lever 130. As shown in FIGS. 1 and 2, the second trip lever 130 has a hook-like configuration and is itself at one end pivotally secured about a vertical axis to an end of a transverse support member 134 which is mounted on the top of upstanding brackets 28 and normally utilized to support the forward, bale-receiving portion of the second table 22. The other end of the second trip lever 130, as clearly shown in FIG. 2, extends upwardly between and above the transverse beams 32,34 of the first table 16 slightly inwardly from the edges of the beams 32,34 at the end of the first table 16 which is opposite to that end of the table 16 at which bales are received.

At the pivotal connection between the outer end of the tab portion 116 of the latch 110 and the link rod 132, indicated as numeral 136, a thin plate 138 is also pivotally secured to the link rod 132 and links the rod 132 and the latch 108 to a extension spring 140 which is linked at its opposite end by a similar second thin plate 142 to the pivotal connection between the rod 124 and the flange 122. The extension spring 140 imposes a bias on the trip lever 128, the second trip lever 130, the locking plate 120, and the latch 110 which normally retain the aforementioned parts of the trip mechanism 104 in what may be characterized, in an overall sense, as a locked condition, as shown in FIGSv In the aforementioned locked condition, the latch 110 of the trip mechanism 104 is coupled to the stop element 102 so as to retain the stop element 102 at the aforemention blocking location. An elongated rod 144 is pivotally coupled at its one end to the latch 110 and at its opposite end to a protruding element 146 fixedly secured to the bottom end of a sleeve 148 rotatable about a vertical axis and mounted about a bracketed shaft 150 being mounted on the left longitudinal rail 14 of the chassis 12. The stop element 102 is fixedly secured to the top end of the rotatable sleeve 148.

Upon receipt of one bale on the first table 16, the trip lever 128 is deflected as described hereinbefore which pivots the locking plate 120 from its locking position of FIG. 3 to its lower unlocking position of FIG. 5. However, deflection of trip lever 128 and the resulting pivotal movement of plate 120 as caused by contact with only a single bale will not in and of itself cause clockwise pivotal movement of latch 110. Because in the preferred form of the improved bale wagon 10 it is desired to receive two bales before the table 16 is operated whereby the distance between the trip lever 128 and the second trip lever 130 is substantially greater than the length of a single bale but less than the combined length of two bales, a second bale must be received on the first table 16 after the first bale which will drive the first bale to the opposite end of the first table 16 in order to engage the second trip lever 130 and pivot it in a clockwise direction about its vertical axis to cause the latch to pivot clockwise and through elongated rod 144 cause the stop element 102 to pivot clockwise out of the path of revolution of the first pawl element 86. Even if a single bale after being received on the first table 16 should be bounced or jostled across the table 16 and engaged with the second trip lever 130, as soon as the bale passes the trip lever 128 in its movement across the table 16 the deflected lever 128 will return to its biased, undeflected position because of the force imposed thereon by extension spring 140 and locking plate will return to its locking position before the single bale arrives at the opposite end of the table 16 and engages the second trip lever 130. Therefore, a single bale is unable to engage the second trip lever so as to pivotally move it. Only when a second bale is received on the table 16 behind the first bale, which second bale will deflect the trip lever 128 to unlock the locking plate 120 and maintain the trip lever 128 in its deflected position as the second bale is driven by the conveyor 18 against the first bale, will the first bale be able to engage and pivotally move the second trip lever 130. Therefore, upon the aforementioned pivotal movement of the levers 128,130 and resulting pivotal movement of the locking plate 120 and the latch 110 to what may be characterized, in an overall sense, as an unlocked condition as shown in FIGS. 5 and 6 and as caused by the receipt of two bales on the first table 16, the stop element 102 is pivoted out of the path of revolution of the first pawl element 86 whereby, in the manner described hereinbefore, the driven input component 70 will automatically become operatively coupled to the driving input component 52 via the automatic engagement provided by the biased first pawl element 86 between the first and second clutch members 56,74. Rotation of the shaft 72 of the driven com ponent 70 carries with it revolution of the free end 82 of the crank arm 76 about the rotational axis A of the shaft 72. Revolution of the free end 82 of the crank arm 76 drives the first table 16 through the linking member 78 and thereby causes pivotal movement of the first table 16 from its lower, bale-receiving position toward its upper, bale-discharge position. It is readily apparent that as soon as the first table leaves its lower position,

the engagements of the two bales being carried thereon with the trip levers 128,130 are released and thereby the bias being imposed on the levers 128,130 by the spring 140 returns the levers to their initial positions, characterized hereinabove as their locked conditions, wherein they will be now ready for the return of the first table 16 to its lower position and the conveyance of two more bales to the table 16 by the bale loader and the conveyor 18. Also, it is readily apparent that the return of the levers 128,130 to their locked condition which occurs prior to the completion of one pivotal cycle by the table 16 carries with it the counterclockwise pivotal movement of the stop element 102 back to its initial blocking location in the path of revolution of the first pawl element 86 prior to the completion of one revolution by the first pawl element 86 along its path about axis A The pawl element 86 is thus prevented by the stop element 102 from making more than one revolution at a time. Accordingly, the second clutch member 74 can only be maintained by the pawl element 86 in engagement with the first clutch member 56 and rotate therewith about axis A for one rotation cycle of the first clutch member 56. It follows therefrom that only one complete cycle of pivotal movement of the first table 16 between its upper and lower positions is allowed at a time. IMPROVED PIVOTAL MOVEMENT OF THE FIRST TABLE BY THE DRIVE ASSEMBLY Referring now to FIGS. 9A 9F, there is illustrated successive positions of the first table 16 (carrying bales B) at successive points in time during its pivotal movement from its lower position to its upper position when the first table 16 is operated by the driving unit 48 of the drive assembly 46 of the present invention, as depicted in solid line, in comparison with successive positions of the first table designated as 16', (carrying bales B) at identical successive points in time during its pivotal movement from its lower position to its upper position when the first table 16' is operated by a hydraulic cylinder 152, as depicted in broken line, utilized heretofore in the prior art. The cylinder is shown pivotally mounted at point P which is identical to the initial po sition of the point of linkage P between the linking member 78 and the crank arm 76 of the driving unit 48. At the outset, it should be noted that, at POSITION of FIG. 9A, both first tables 16 and 16' are disposed at their lower, substantially horizontal, bale-receiving position identical to that of FIG. 2 and, at POSITION of FIG. 9F, both first tables 16 and 16 are disposed at their upper, substantially vertical, bale-discharge position. Further, it should be noted that, in the successive positions as illustrated in FIGS. 9A 9F with respect to both the case of the driving unit/ first table operation and the case of the hydraulic cylinder/ first table operation, the respective periods of elapsed time from POSI- TION -0- of FIG. 9A to POSITION -1- of FIG. 9B, from POSITION -1- of FIG. 98 to POSITION -2- of FIG. 9C, from POSITION -2- of FIG. 9C to POSITION -3- of FIG. 9D, from POSITION -3- of FIG. 9D to POSITION -4- of FIG. 9E, and from POSITION -4- of FIG. 9E to POSITION -5- of FIG. 9F are all of equal duration.

Therefore, since the successive periods of elapsed time are equal and may therefore treated as a constant factor, the different and improved pattern of motion imposed on the first table 16 by the driving unit 48 over that pattern imposed on the first table 16 by the hydraulic cylinder 152 may be illustrated by a comparison of the successive angular displacements of the first table 16 as caused by the driving unit 48 with the successive angular displacements of the first table 16 as caused by the hydraulic cylinder 152.

Accordingly, FIG. 98 illustrates the POSITION -lof the solid line first table 16 after the driving unit 48 has rotated (as represented by point P about axis A through one-fifth of that portion of its clockwise rotation cycle in which it positively drives the table 16 from its lower position toward its upper position (or 33 of an approximately portion of one rotation cycle as illustrated in FIG. 10), and also illustrates the POSI- TION -1- of the broken line first table 16' after a piston rod 154 of the hydraulic cylinder 152 has been extended through one-fifth of its total forward driving stroke (the distance between adjacent points P located on the rod 154 indicate one-fifth of the total forward stroke displacement by the rod 154 of the cylinder 152 in pivotally moving the broken line first table 16' from its lower position to its upper position). It is readily apparent in FIG. 9B that the broken line first table 16' has undergone a greater angular displacement than the solid line first table 16 in their pivotal movement about their axis A,, from POSITION -0- to POSITION -1-. FIG. 10 shows that the angular displacement of the broken line first table 16' (as taken along the path of point P being the point of linkage between piston rod 154 and arm 36 of first table 16) was approximately 25 while the corresponding angular displacement of the solid line first table 16 (as taken along the path of P being the point of linkage between linking member 78 and arm 36 of the first table 16) was approximately 17.

FIG. 9C, 9D and 9E illustrate respectively the POSI- TION -2-, POSITION-3- and POSITION -4- of the solid line first table 16 after the driving unit 48 has rotated about axis A consecutively through two-fifths, threefifths, and four-fifths respectively of the aforementioned driving portion of its clockwise rotation cycle (or approximately 66, 99 and 132 respectively as illustrated in FIG. 10), and also illustrate respectively the POSITION -2-, POSITION -3- and POSITION -4- of the broken line first table 16 after the piston rod 154 has been extended consecutively through twofifths, three-fifths and four-fiths respectively of its aforementioned total forward driving stroke. It is readily apparent in viewing FIGS. 9C. 9D and 9E in sequence together that the solid line first table 16 has now undergone a greater angular displacement than the broken line first table 16 in their pivotal movement about their axis A from POSITION -1- to POSITION -4-. FIG. 10 shows that the consecutive angular displacements of the solid line first table 16 were approximately 20, 23 and 23 while the corresponding consecutive angular displacements of the broken line first table 16' were 17, 16V2 and l6 /2.

Finally, FIG. 9F illustrates the POSITION -5- of the solid line first table 16 after the driving unit 48 has rotated about axis A through the final one-fifth of the aforementioned driving portion of its clockwise rotation cycle (or has reached the 165 degree mark as illustrated in FIG. 10) which is approximately identical to the POSITION -5- of the broken line first table 16 after the piston rod 154 has been fully extended through the final one-fifth of its aforementioned total forward driving stroke. It is readily apparent in viewing FIGS. 9E and 9F in sequence together that the broken line first table 16' has now undergone a greater angular displacement than the solid line first table 16 in their pivotal movement about their axis A from POSITION -4- to POSITION -5-. FIG. I shows that the angular displacement of the broken line first table 16 was approximately l9 while the corresponding angular displacement of the solid line first table 16 was approximately 11.

Where the factor of time is treated as constant, the average angular velocities between consecutive ones of POSITION -0- to POSITION of the solid line and broken line first table 16 and 16' are directly proportional to their angular displacements therebctween. Therefore, in comparison with each other, the average angular velocity of the solid line first table 16 is substantially less than that of the broken line first table 16' during pivotal movement of the first table 16 and 16' from POSITION -0- to POSITION -land from POSI- TION -4- to POSITION -5-, or during what may be respectively characterized as initial and final portions of their pivotal movements from their lower position to their upper position. Also, in comparison with each other, the average angular velocity of the solid line first table 16 is substantially greater than that of the broken line first table 16' during pivotal movement of the first tables 16 and 16 from POSITION -I- through POSI- TION -2- and POSITION -3- to POSITION -4-, or during what may be characterized as an intermediate portion of their pivotal movements from their lower positions to their upper positions. Further, in comparison with itself, the solid line first table 16 is driven by the driving unit 48 at significantly lower average angular velocities during its pivotal movement from POSITION -0- to POSITION -land from POSITION -4- to POSI- TION -5-, or respectively during the initial and final portions of its pivotal movement, and at a significantly higher average angular velocity during its pivotal movement from POSITION -1- through POSITION -2- and POSITION -3- to POSITION -4-, or during the intermediate portion of its pivotal movement. In constract, when compared with itself, the broken line first table [6' is driven by the hydraulic cylinder 152 at signifi cantly higher average angular velocities during its pivotal movement from POSITION -0- to POSITION -1- and from POSITION -4- to POSITION -5-, or respectively during the initial and final portions of its pivotal movement, and at a significantly lower average angular velocity during its pivotal movement from POSITION -I- through POSITION -2- and POSITION -3- to POSI- TION -4-, or during the intermediate portion of its pivotal movement.

The aforementioned pattern of average angular velocities imposed on the first table 16 by the driving unit 48, in contrast to the undesirable pattern imposed thereon by the hydraulic cylinder 152 utilized heretofore in the prior art, imparts an increasing momentum to the bales B being carried on the first table 16 to thereby maintain the bales at rest in the aforementioned desired arrangement, substantially as they were received initially on the first table 16, during the first and intermediate portions of its pivotal movement from its bale-receiving position toward its bale-discharge position and appropriately reduces the momentum being imparted to the bales B during the final portion of pivotal movement of the first table 16 to achieve depositing of the bales B on the forward, bale-receiving portion 20 of the second table 22 in the aforementioned arrangement when the first table reaches its baledischarge position which arrangement of the bales B enchances the efficient performance of the subsequent tier-forming operation of the second table 22. Therefore, referring to FIGS. 10 and 11, it should be noted that while points P, and P both fall on respective straight lines which are tangent to the arcs of pivotal movement of first tables 16 and 16' (as represented by the paths of revolution of points P and P respectively) at locations within the aforementioned intermediate portions of their pivotal movement, the first table 16 undergoes its maximum velocities during this portion of its pivotal movement while the first table 16 undergoes its minimum velocities during this portion of its pivotal movement.

After the first table 16 has reaches its upper, baledischarge position, it begins its reverse pivotal movement back to its initial lower, bale-receiving position. Because of the weight of the first table 16, there would ordinarily be a tendency for the descending table to cause the second clutch member 74 to overrun the first clutch member 56 as will be understood by those skilled in the art. However, as the second clutch member 74 of the driving unit 48 proceeds on its reverse or return portion of its rotation cycle, centrifugal as well as gravitational forces cause the second pawl element 88 to pivot outwardly toward the inner periphery 68 of the annular ring portion 66 of the first clutch member 56 until the roller 92 of the second pawl element 88 becomes disposed in the aforementioned closely=fitted, engaged relationship with one of the recesses 93 in the periphery 68 as shown in FIG. 8. The second pawl element 88 will remain at its outward position until the second clutch member 74 completes its rotational cycle to its initial position of FIG. 2 at which time the unbiased second pawl element 88 drops back to its inward position because of the influence of the force of gravity.

It will be obvious to those skilled'in the art that the first table 16 may be adapted to receive one bale or three bales, rather than two bales and that the trip mechanism 104 of the control component 50 may be modified accordingly to automatically operatively couple the driven output component of the driving unit 48 with the driving input component 52 after one bale or three bales are received on the first table 16, instead of after two bales are received. Further, it will be obvious to those skilled in the art that the drive assembly 46 can likewise be incorporated into a self-propelled bale wagon, rather than a bale wagon intended to be pulled by a tractor, and utilize the power takeoff of the selfpropelled wagon.

It is through that the invention and many of its attendant advantages will be understood from the foregoing description and it will be apparent that various changes may be made in the form, construction and arrangement of the parts without departing from the spirit and scope of the invention or sacrificing all of its material advantages, the form hereinbefore described being merely a preferred or exemplary embodiment thereof. Having thus described the invention, what is claimed 1. An improved bale wagon of the type which includes a chassis, a first table pivotally mounted on said chassis and capable of receiving a predetermined number of bales thereon and capable of being pivotally moved forwardly and reversely along a path of revolution defined about an axis along which said first table is pivotally mounted on said chassis between a lower, substantially horizontal. bale-receiving position and an upper, substantially vertical, bale-discharge position, and a second table mounted on said chassis and capable of receiving said bales from said first table when said first table is at its bale-receiving position, wherein the improvement comprises:

a mechanical drive assembly mounted on said chassis for pivotally moving said first table forwardly and reversely along its path of revolution between its said positions, said assembly including a driving input component capable of being coupled to an external source of rotary power, such as a power takeoff of a tractor, and continuously rotatably driven thereby at a substantially constant rotational velocity,

a driven output component coupled to said first table and capable of being inoperatively uncoupled from said driving input component and capable of being operatively coupled to, and driven by, said driving input component, said driven output component when operatively coupled to said driving input component translating said rotation of said driving input component into reciprocatory movement to cause said pivotal movement of said first table through one complete cycle forwardly along said path of revolution thereof from its bale-receiving position to its bale-discharge position, and reversely along said path of revolution thereof back to its bale-receiving position, for each single rotational cycle of said driving input component, and

a control component capable of maintaining said driven output component inoperatively uncoupled from said driving input component prior to each time said bales have been received on said first table at its bale-receiving position and capable of allowing operative coupling of said driven output component to said driving input component during only a single rotation cycle thereof each time after said bales have been received on said first table for pivotally moving said first table through only one complete cycle, said driven output component when operatively coupled to said driving input component for said single rotation cycle thereof imposing a relatively low average angular velocity on said first table during an initial portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its baledischarge position, a relatively high average angular velocity on said first table during an intermediate portion ofits pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and a relatively low average angular velocity on said first table during a final portion of its pivotal movement forwardly along said path of revolution from its balereceiving position to its bale-discharge position,

whereby said bales being carried by said first table are imparted with an increasing momentum, and thereby maintained at rest in a desired arrangement on said first table substantially as received thereon, during said initial and intermediate portions of said first table pivotal movement forwardly along said path of revolution from its balereceiving position to its bale-discharge position and are imparted with a decreasing momentum, and thereby deposited on said second table in said arrangement, during said final portion of said first table pivotal movement forwardly along said path of revolution when said first table reaches its baledischarge position.

2. An improved bale wagon of the type which includes a chassis, a first table pivotally mounted on said chassis and capable of receiving a predetermined number of bales thereon and capable of being pivotally moved forwardly andvreversely along a path of revolution defined about an axis along which said first table is pivotally mounted on said chassis between a lower, substantially horizontal, bale-receiving position and an upper, substantially vertical. bale-discharge position, and a second table mounted on said chassis and capable of receiving said bales from said first table when said first table is at its bale-receiving position, wherein the improvement comprises:

a mechanical drive assembly mounted on said chassis for pivotally moving said first table forwardly and reversely along its path of revolution between its said position, said assembly including a driving input component capable of being coupled to an external source of rotary power, such as a power takeoff of a tractor, and continuously rotatably driven thereby at a substantially constant rota tional velocity,

a driven output component capable of being operatively uncoupled from said driving input component and capable of being operatively coupled to, and rotatably driven by, said driving input component about an axis of rotation, said driven output component including a shaft rotatably mounted on said chassis for rotation about said axis of rotation of said driven output component,

a crank arm fixed to said shaft and extending outwardly therefrom to a free end which revolves about said axis of rotation as said shaft rotates about said axis, and

a linking member pivotally coupled at one end to said free end of said crank arm at a first point offset from said rotational axis of said shaft, pivotally coupled at an opposite end to said first table at a second point offset from said axis of revolution of said first table through a distance which is substantially greater than the distance through which said first point is offset from said rotational axis of said shaft, and having a length which is substantially greater than said respective distances of offset, such that, when said driven output component is operatively coupled to, and rotated through one rotation cycle by, said driving input component, said one end of said linking member at its said first point pivots with respect to said free end of said crank arm and revolves through one revolution cycle about said rotational axis of said shaft concurrently with said rotation of said shaft for each single rotational cycle of said driven output component and said opposite end of said linking member at its said second point pivots with respect to said first table and concurrently therewith pivotally moves said first table through one complete reciprocatory cycle about its said axis of revolution forwardly along said path of revolution from its balereceiving position to its bale-discharge position and reversely back along said path of revolution to its bale-receiving position for each single rotational cycle of said driven output component; and g a control component capable of maintaining said driven output component inoperatively uncoupled from said driving input component prior to each time said bales have been received on said first table at its bale-receiving position and capable of allowing operative coupling of said driven output component to said driving input component during only a single rotation cycle thereof for causing rotation of said driven output component through only one rotational cycle thereof each time after said bales have been received on said first table for pivotally moving said first table through only one complete reciprocatory cycle via said linking member, said driven output component when operatively coupled to, and rotated through one rotational cycle by, said driving input component imposing via said linking member a relatively low average angular velocity on said first table during an initial portion of its pivotal movement forwardly along said path of revolution from its balereceiving position to its bale-discharge position, a relatively high average angular velocity on said first table during an intermediate portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its baledischarge position and a relatively low average angular velocity on said first table during a final portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position,

whereby said bales being carried by said first table are imparted with an increasing momentum, and

thereby maintained at rest in a desired arrange ment on said first table substantially as received thereon, during said initial and intermediate portions of said first table movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and are imparted with a decreasing momentum, and thereby deposited on said second table in said arrangement, during said final portion of said first table movement forwardly along said path of revolution when said first table reaches its bale-discharge position.

3. An improved bale wagon of the type which includes a chassis, a first table pivotally mounted on said chassis and capable of receiving a predetermined number of bales thereon and capable of being pivotally moved forwardly and reversely along a path of revolution defined about an axis along which said first table is pivotally mounted on said chassis between a lower, substantially horizontal, bale-receiving position and an upper, substantially vertical, bale-discharge position, and a second table mounted on said chassis and capable of receiving said bales from said first table when said first table is at its bale-receiving position, wherein the improvement comprises:

a mechanical drive assembly mounted on said chassis for pivotally moving said first table forwardly and reversely along its path of revolution between its said positions, said assembly including a first clutch member capable of being coupled to an external source of rotary power, such as a power takeoff of a tractor, and continuously rotatably driven thereby at a substantially constant rotational velocity,

a shaft rotatably mounted about an axis on said chassis with said first clutch member rotatably mounted thereon,

a second clutch member fixedly mounted on said shaft for rotation therewith and having a pawl means pivotally mounted thereon for engagement with, and disengagement from said first clutch member and normally biased to be engaged with said first clutch member for causing rotation of said second clutch member and said shaft with said first clutch member. said pawl means movable about said axis of said shaft through a path of revolution concurrently with rotation of said shaft and said second clutch member about said shaft axis when said pawl means is engaged with said first clutch member,

a crank arm fixed to said shaft and extending out wardly therefrom to a free end which revolves about said shaft axis as said shaft rotates about said axis,

a linking member pivotally coupled at one end to said free end of said crank arm at a-first point offset from said rotational axis of said shaft, pivotally coupled at an opposite end to said first table at a second point offset from said axis of revolution of said first table through a distance which is substantially greater than the distance through which said first point is offset from said rotational axis of said shaft, and having a length which is substantially greater than said respective distances of offset, such that, when said pawl means is engaged with said first clutch member, and thereby said second clutch member and said shaft are rotated, and said crank arm is revolved, about said shaft axis through one cycle by said first clutch member, said one end of said linking member at its said first point pivots with respect to said free end of said crank arm and revolves through one revolution cycle about said shaft axis and said opposite end of said linking member at its said second point pivots with respect to said first table and concurrently therewith pivotally moves said first table through one complete reciprocatory cycle about its said axis of revolution forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and reversely back along said path of revolution to its bale-receiving position for each single rotational cycle of said engaged first and second clutch members and said shaft,

a pawl stop means pivotally mounted on said chassis and movable between one location along said path of revolution of said pawl means, at which location it blocks said path and is engaged with said pawl means when said pawl means is at said one location to thereby maintain said pawl means against its bias and disengaged from said first clutch member, and another location outside of said path of revolution of said pawl means, at which location it is disengaged from said pawl means to allow said bias of said pawl means to automatically engage it with said first clutch member, and

a trip mechanism biased to normally maintain said pawl stop means at said one location, said mechanism responding to engagement by said bales when said bales are at rest in their desired arrangement on said first table with said first table being in its bale receiving position to pivotally move said pawl stop means from its one location to its other location, said bias of said mechanism causing said pawl stop means to return to its one location, immediately after said first table begins to be pivotally moved from its said bale-receiving position and before it completes its one cycle of movement back to its bale-receiving position, due to disengagement of said bales from said mechanism as caused by said table movement, said immediate return of said pawl stop means to its one location thereby preventing said pawl means from revolving about its path of revolution for more than one cycle which as a result allows only one reciprocatory cycle of movement of said first table at a time, said second clutch member when engaged via said pawl means with said first clutch member, and rotated thereby through one rotational cycle, imposing via said concurrent rotation of said shaft, and revolution of said crank arm and said one end of said linking member, therewith a relatively low average angular velocity on said first table during an initial portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position, a relatively high average angular velocity on said first table during an intermediate portion of its pivotal movement forwardly along said path of revolution from its balereceiving position to its bale-discharge position and a relatively low average angular velocity on said first table during a final portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position,

whereby said bales being carried by said first table are imparted with an increasing momentum. and thereby maintained at rest in a desired arrangement on said first table substantially as received thereon, during said initial and intermediate portions of said first table movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and are imparted with a decreasing momentum, and thereby deposited on said second table in said arrangement, during said final portion of said first table movement forwardly along said path of revolution when said first table reaches its bale-discharge position. 

1. An improved bale wagon of the type which includes a chassis, a first table pivotally mounted on said chassis and capable of receiving a predetermined number of bales thereon and capable of being pivotally moved forwardly and reversely along a path of revolution defined about an axis along which said first table is pivotally mounted on said chassis between a lower, substantially horizontal, bale-receiving position and an upper, substantially vertical, bale-discharge position, and a second table mounted on said chassis and capable of receiving said bales from said first table when said first table is at its bale-receiving position, wherein the improvement comprises: a mechanical drive assembly mounted on said chassis for pivotally moving said first table forwardly and reversely along its path of revolution between its said positions, said assembly including a driving input component capable of being coupled to an external source of rotary power, such as a power takeoff of a tractor, and continuously rotatably driven thereby at a substantially constant rotational velocity, a driven output component coupled to said first table and capable of being inoperatively uncoupled from said driving input component and capable of being operatively coupled to, and driven by, said driving input component, said driven output component when operatively coupled to said driving input component translating said rotation of said driving input component into reciprocatory movement to cause said pivotal movement of said first table through one complete cycle forwardly along said path of revolution thereof from its balereceiving position to its bale-discharge position, and reversely along said path of revolution thereof back to its bale-receiving position, for each single rotational cycle of said driving input component, and a control component capable of maintaining said driven output component inoperatively uncoupled from said driving input component prior to each time said bales have been received on said first table at its bale-receiving position and capable of allowing operative coupling of said driven output component to said driving input component during only a single rotation cycle thereof each time after said bales have been received on said first table for pivotally moving said first table through only one complete cycle, said driven output component when operatively coupled to said driving input component for said single rotation cycle thereof imposing a relatively low average angular velocity on said first table during an initial portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position, a relatively high average angular velocity on said first table during an intermediate portion of its pivotal movement forwardly along said path of revolution from its balereceiving position to its bale-discharge position and a relatively low average angular velocity on said first table during a final portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position, whereby said bales being carried by said first table are imparted with an increasing momentum, and thereby maintained at rest in a desired arrangement on said first table substantially as received thereon, during said initial and intermediate portions of said first table pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and are imparted with a decreasing momentum, and thereby deposited on said second table in said arrangement, during said final portion of said first table pivotal movement forwardly along said path of revolution when said first table reaches its bale-discharge position.
 2. An improved bale wagon of the type which includes a chassis, a first table pivotally mounted on said chassis and capable of receiving a predetermined number of bales thereon and capable of being pivotally moved forwardly and reversely along a path of revolution defined about an axis along which said first table is pivotally mounted on said chassis between a lower, substantially horizontal, bale-receiving position and an upper, substantially vertical, bale-discharge position, and a second table mounted on said chassis and capable of receiving said bales from said first table when said first table is at its bale-receiving position, wherein the improvement comprises: a mechanical drive assembly mounted on said chassis for pivotally moving said first table forwardly and reversely along its path of revolution between its said position, said assembly including a driving input component capable of being coupled to an external source of rotary power, such as a power takeoff of a tractor, and continuously rotatably driven thereby at a substantially constant rotational velocity, a driven output component capable of being operatively uncoupled from said driving input component and capable of being operatively coupled to, and rotatably driven by, said driving input component about an axis of rotation, said driven output component including a shaft rotatably mounted on said chassis for rotation about said axis of rotation of said driven output component, a crank arm fixed to said shaft and extending outwardly therefrom to a free end which revolves about said axis of rotation as said shaft rotates about said axis, and a linking member pivotally coupled at one end to said free end of said crank arm at a first point offset from said rotational axis of said shaft, pivotally coupled at an opposite end to said first table at a second point offset from said axis of revolution of said first table through a distance which is substantially greater than the distance through which said first point is offset from said rotational axis of said shaft, and having a length which is substantially greater than said respective distances of offset, such that, when said driven output component is operatively coupled to, and rotated through one rotation cycle by, said driving input component, said one end of said linking member at its said first point pivots with respect to said free end of said crank arm and revolves through one revolution cycle about said rotational axis of said shaft concurrently with said rotation of said shaft for each single rotational cycle of said driven output component and said opposite end of said linking member at its said second point pivots with respect to said first table and concurrently therewith pivotally moves said first table through one complete reciprocatory cycle about its said axis of revolution forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and reversely back along said path of revolution to its bale-receiving position for each single rotational cycle of said driven output component; and a control component capable of maintaining said driven output component inoperatively uncoupled from said driving input component prior to each time said bales have been received on said first table at its bale-receiving position and capable of allowing operative coupling of said driven output component to said driving input component during only a single rotation cycle thereof for causing rotation of said driven output component through only one rotational cycle thereof each time after said bales have been received on said first table for pivotally moving said first table through only one complete reciprocatory cycle via said linking member, said driven output component when operatively coupled to, and rotated through one rotational cycle by, said driving input component imposing via said linking member a relatively low average angular velocity on said first table during an initial portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position, a relatively high average angular velocity on said first table during an intermediate portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and a relatively low average angular velocity on said first table during a final portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position, whereby said bales being carried by said first table are imparted with an increasing momentum, and thereby maintained at rest in a desired arrangement on said first table substantially as received thereon, during said initial and intermediate portions of said first table movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and are imparted with a decreasing momentum, and thereby deposited on said second table in said arrangement, during said final portion of said first table movement forwardly along said path of revolution when said first table reaches its bale-discharge position.
 3. An improved bale wagon of the type which includes a chassis, a first table pivotally mounted on said chassis and capable of receiving a predetermined number of bales thereon and capable of being pivotally moved forwardly and reversely along a path of revolution defined about an axis along which said first table is pivotally mounted on said chassis between a lower, substantially horizontal, bale-receiving position and an upper, substantially vertical, bale-discharge position, and a second table mounted on said chassis and capable of receiving said bales from said first table when said first table is at its bale-receiving position, wherein the improvement comprises: a mechanical drive assembly mounted on said chassis for pivotally moving said first table forwardly and reversely along its path of revolution Between its said positions, said assembly including a first clutch member capable of being coupled to an external source of rotary power, such as a power takeoff of a tractor, and continuously rotatably driven thereby at a substantially constant rotational velocity, a shaft rotatably mounted about an axis on said chassis with said first clutch member rotatably mounted thereon, a second clutch member fixedly mounted on said shaft for rotation therewith and having a pawl means pivotally mounted thereon for engagement with, and disengagement from said first clutch member and normally biased to be engaged with said first clutch member for causing rotation of said second clutch member and said shaft with said first clutch member, said pawl means movable about said axis of said shaft through a path of revolution concurrently with rotation of said shaft and said second clutch member about said shaft axis when said pawl means is engaged with said first clutch member, a crank arm fixed to said shaft and extending outwardly therefrom to a free end which revolves about said shaft axis as said shaft rotates about said axis, a linking member pivotally coupled at one end to said free end of said crank arm at a first point offset from said rotational axis of said shaft, pivotally coupled at an opposite end to said first table at a second point offset from said axis of revolution of said first table through a distance which is substantially greater than the distance through which said first point is offset from said rotational axis of said shaft, and having a length which is substantially greater than said respective distances of offset, such that, when said pawl means is engaged with said first clutch member, and thereby said second clutch member and said shaft are rotated, and said crank arm is revolved, about said shaft axis through one cycle by said first clutch member, said one end of said linking member at its said first point pivots with respect to said free end of said crank arm and revolves through one revolution cycle about said shaft axis and said opposite end of said linking member at its said second point pivots with respect to said first table and concurrently therewith pivotally moves said first table through one complete reciprocatory cycle about its said axis of revolution forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and reversely back along said path of revolution to its bale-receiving position for each single rotational cycle of said engaged first and second clutch members and said shaft, a pawl stop means pivotally mounted on said chassis and movable between one location along said path of revolution of said pawl means, at which location it blocks said path and is engaged with said pawl means when said pawl means is at said one location to thereby maintain said pawl means against its bias and disengaged from said first clutch member, and another location outside of said path of revolution of said pawl means, at which location it is disengaged from said pawl means to allow said bias of said pawl means to automatically engage it with said first clutch member, and a trip mechanism biased to normally maintain said pawl stop means at said one location, said mechanism responding to engagement by said bales when said bales are at rest in their desired arrangement on said first table with said first table being in its bale receiving position to pivotally move said pawl stop means from its one location to its other location, said bias of said mechanism causing said pawl stop means to return to its one location, immediately after said first table begins to be pivotally moved from its said bale-receiving position and before it completes its one cycle of movement back to its bale-receiving position, due to disengagement of said bales from said mechanism as caused by said table movement, said immediate return of said pawl stop means to its one location thereby preventing said pawl means from revolvIng about its path of revolution for more than one cycle which as a result allows only one reciprocatory cycle of movement of said first table at a time, said second clutch member when engaged via said pawl means with said first clutch member, and rotated thereby through one rotational cycle, imposing via said concurrent rotation of said shaft, and revolution of said crank arm and said one end of said linking member, therewith a relatively low average angular velocity on said first table during an initial portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position, a relatively high average angular velocity on said first table during an intermediate portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and a relatively low average angular velocity on said first table during a final portion of its pivotal movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position, whereby said bales being carried by said first table are imparted with an increasing momentum, and thereby maintained at rest in a desired arrangement on said first table substantially as received thereon, during said initial and intermediate portions of said first table movement forwardly along said path of revolution from its bale-receiving position to its bale-discharge position and are imparted with a decreasing momentum, and thereby deposited on said second table in said arrangement, during said final portion of said first table movement forwardly along said path of revolution when said first table reaches its bale-discharge position. 